US8226518B2 - Continually variable transmission - Google Patents

Continually variable transmission Download PDF

Info

Publication number
US8226518B2
US8226518B2 US11/916,484 US91648405A US8226518B2 US 8226518 B2 US8226518 B2 US 8226518B2 US 91648405 A US91648405 A US 91648405A US 8226518 B2 US8226518 B2 US 8226518B2
Authority
US
United States
Prior art keywords
epicyclic gear
satellite
gear
sun
coupled
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related, expires
Application number
US11/916,484
Other versions
US20090023532A1 (en
Inventor
Javier Parraga Gimeno
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
POWERTRACK INTERNATIONAL DE AUTOMOCION SL
Original Assignee
Power Gear SL
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Power Gear SL filed Critical Power Gear SL
Assigned to POWER GEAR S.L. reassignment POWER GEAR S.L. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GIMENO, JAVIER PARRAGA
Publication of US20090023532A1 publication Critical patent/US20090023532A1/en
Assigned to POWERTRACK INTERNATIONAL DE AUTOMOCION S.L. reassignment POWERTRACK INTERNATIONAL DE AUTOMOCION S.L. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: POWER GEAR S.L.
Application granted granted Critical
Publication of US8226518B2 publication Critical patent/US8226518B2/en
Expired - Fee Related legal-status Critical Current
Adjusted expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H37/0846—CVT using endless flexible members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • F16H2037/088—Power split variators with summing differentials, with the input of the CVT connected or connectable to the input shaft

Definitions

  • the present invention refers to a continually variable transmission, of the type of transmission of movements using variable speed device, one of each has a conical surface.
  • This invention is characterised by its special construction of a transmission with power derivation at the output and to the main motor, incorporating an intercalated differential mechanism which reduces the rotation speed of the intermediate shaft to zero in either direction, thus achieving the advantages of a greater speed variation range, using the high torque transmitted, apart from the financial savings deriving therefrom.
  • this invention generates a discontinuity in the transmission relation between the pair of pulleys, in particular with respect to the shaft speed of the entry and outlet shafts, which leads to a need to change the direction of the outlet shaft when the speed is still relatively high, with subsequent disadvantages in the long term with respect to stress and wear etc.
  • the present invention refers to a continually variable transmission, of the type of transmission of movements using variable speed device and in particular, one of these having a conical surface as well as incorporating epicyclic gears.
  • An external driving couples to the aforementioned variable speed device, partially receiving power from the motor shaft by means of a pinion gear and provided with tapered pulleys both of which connected to a differential mechanism, for example, one of these connected to the crown wheel of an epicyclical gear, while the other pulley is linked to the sun and the satellite carrier of the planetary gear set and transmits that power to a subsequently arranged reducer mechanism.
  • This reducer for example, may be a new epicyclical gear which is arranged intermediately in respect of another outlet device in a similar construction.
  • the reducer of the sun is coupled to the satellite carrier of the differential mechanism.
  • a device which blocks the sun and the satellite carriers of the reducer in this phase permits a transmission ratio of 1:1.
  • the satellite carrier may be blocked with the crown wheel obtaining the same effect.
  • the satellite carrier of the reducer is provided with a means of fixation as a brake so that having established this fixation, the group acts as a reducer.
  • the crown wheel is connected to the sun of the final reduction phase.
  • this outlet device or final phase of reduction identified as third epicyclical gear
  • the satellite carrier is in turn connected to the outlet shaft of the transmission, in this way deriving the aforementioned fraction of the entry power to the two pulleys.
  • the crown wheel of this third epicyclical gear is coupled to the entry shaft.
  • the pulley attached to the motor shaft should be positioned at its maximum diameter with the satellite carrier interlock disconnected and with the sun joined to the satellite carrier.
  • FIG. 1 shows a diagram of the transmission according to a preferred embodiment of the three interconnected epicyclical gears of the invention.
  • the present invention refers to a continually variable transmission, of the type of transmission means using variable speed device and in particular, one of these having a conical surface as well as incorporating epicyclical gears.
  • an external drive ( 1 ) is coupled to the variable speed device ( 2 ) and ( 3 ) connected to an epicyclical gear ( 5 ) partially receiving the power from the motor shaft, by means of a gear pinion ( 4 ) and with the tapered pulley ( 2 ) connected to the crown wheel ( 5 . 1 ) through transmission means ( 10 ) and ( 11 ) in this example, of the epicyclic gear ( 5 ) while the other pulley ( 3 ) is linked to the sun ( 5 . 2 ) and the satellite carrier ( 5 . 3 ) transmits this power to a subsequently arranged epicyclic gear ( 6 ) coupled or interlocked ( 6 . 5 ) with the satellite carrier ( 6 .
  • the satellite carrier ( 6 . 2 ) is coupled to an interlock ( 6 . 3 ) and its crown wheel ( 6 . 4 ) is connected to the sun ( 7 . 1 ) of the epicyclic gear ( 7 ) the satellite carrier of which ( 7 . 2 ) is in turn connected to the outlet shaft ( 8 ) of the transmission, thus deriving from this the aforementioned fraction of the entry power to the two pulleys ( 2 ) and ( 3 ) while the crown wheel ( 7 . 3 ) of this third epicyclical gear ( 7 ) is made with the gear pinion ( 9 ) of the entry shaft.
  • the pulley ( 3 ) In order to obtain reverse gear, the pulley ( 3 ) should be positioned at its maximum diameter, with the interlocking ( 6 . 3 ) of the satellite carrier ( 6 . 2 ) disconnected and connecting the interlock ( 6 . 5 ).
  • a progression of pulley ( 3 ) diameters is made from the diameter closest to maximum to the diameter closest to minimum and with the interlocking ( 6 . 3 ) of the satellite carrier ( 6 . 2 ) disconnected and connected to the interlock ( 6 . 5 ).
  • the fact that the satellite carrier ( 5 . 3 ) outlet speed is zero when the pulley ( 3 ) approximates to its range of minimum diameter is taken advantage of to stop the epicyclical gear satellite carrier ( 6 . 2 ) with the interlocking mechanism ( 6 . 3 ) at zero speed of the intermediate shaft.
  • the pulley ( 3 ) progression is varied in the inverse direction, that is, from its minimum diameter to its maximum diameter.
  • the aforementioned mechanical transmission effectively generates a continual reduction, either a continual multiplication or a continual transmission ratio of 1:1.
  • the epicyclical gear ( 6 ) may be dispensed with, thus joining the satellite carrier ( 5 . 3 ) of the epicyclical gear ( 5 ) with the sun ( 7 . 1 ) of the epicyclical gear ( 7 ).

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
  • Valve Device For Special Equipments (AREA)
  • Containers And Packaging Bodies Having A Special Means To Remove Contents (AREA)

Abstract

Continuously variable transmission is discloses as comprising a continuously variable speed device such that the speed of the final outlet shaft (8) may be varied in any rotation direction and to zero using a combination of different diameters of a first pulley.

Description

OBJECT OF THE INVENTION
The present invention refers to a continually variable transmission, of the type of transmission of movements using variable speed device, one of each has a conical surface.
This invention is characterised by its special construction of a transmission with power derivation at the output and to the main motor, incorporating an intercalated differential mechanism which reduces the rotation speed of the intermediate shaft to zero in either direction, thus achieving the advantages of a greater speed variation range, using the high torque transmitted, apart from the financial savings deriving therefrom.
BACKGROUND TO THE INVENTION
For some years mechanical power systems have been known of the type able to continually change their rate of speed, generally in the range of medium and low power, usually obtained by continual variation of the ratio of the radiuses of two pulleys, in particular in those applications in which their characteristics lend themselves to this type of system, such as agricultural machinery and also the “gear box” of all kinds of vehicles.
Another related registration is U.S. Pat. No. 6,517,461 in the name of Nissan Motor Co., which consists of a transmission mechanism incorporating a helical gear which meshes with a final outlet gear which transmits rotation to the final mechanism of the shaft, with the sides of the teeth and the final outlet the final output shaft of a ring gear arranged in such a way that the force exercised on the ring by a planetary gear and the force exercised by the transmission act in opposite directions.
In the automotive field patent ES 2068047 may also be cited: “Continual mechanical gear change” which incorporates a pair of tapered pulleys, with an intermediate flexible transmission element together with a power transmission mechanism and a planetary gear arranged at the outlet connecting, the first pulley to the entry shaft of the system, while the second is connected to the entry shaft of the power transmission mechanism, the outlet shaft of which activates one of the planetary elements while the remaining elements are related respectively with the entry shaft and the outlet shaft of the device which is the object of the invention, in various arrangements and distributions of these elements.
Despite its validity and opportunity, this invention generates a discontinuity in the transmission relation between the pair of pulleys, in particular with respect to the shaft speed of the entry and outlet shafts, which leads to a need to change the direction of the outlet shaft when the speed is still relatively high, with subsequent disadvantages in the long term with respect to stress and wear etc.
The applicant is unaware of mechanical transmissions which are genuinely continual and with a high range of variation of revolutions of the outlet shaft, in addition to high torque, which resolve the aforementioned problem by incorporating a differential mechanism which dispenses with the need for reverse gear and clutch, and which also resolves this problem with the simplicity and effectiveness of the invention described herein.
DESCRIPTION OF THE INVENTION
The present invention refers to a continually variable transmission, of the type of transmission of movements using variable speed device and in particular, one of these having a conical surface as well as incorporating epicyclic gears.
An external driving couples to the aforementioned variable speed device, partially receiving power from the motor shaft by means of a pinion gear and provided with tapered pulleys both of which connected to a differential mechanism, for example, one of these connected to the crown wheel of an epicyclical gear, while the other pulley is linked to the sun and the satellite carrier of the planetary gear set and transmits that power to a subsequently arranged reducer mechanism.
This reducer, for example, may be a new epicyclical gear which is arranged intermediately in respect of another outlet device in a similar construction.
The reducer of the sun is coupled to the satellite carrier of the differential mechanism. A device which blocks the sun and the satellite carriers of the reducer in this phase permits a transmission ratio of 1:1. Optionally, the satellite carrier may be blocked with the crown wheel obtaining the same effect.
The satellite carrier of the reducer is provided with a means of fixation as a brake so that having established this fixation, the group acts as a reducer. The crown wheel is connected to the sun of the final reduction phase.
In this outlet device or final phase of reduction, identified as third epicyclical gear the satellite carrier is in turn connected to the outlet shaft of the transmission, in this way deriving the aforementioned fraction of the entry power to the two pulleys. It will be seen that in an example of an embodiment the crown wheel of this third epicyclical gear is coupled to the entry shaft.
In order to reduce the speed of the outlet shaft of the final epicyclical gear in any of its directions to zero, to this transmission construction described with, on one hand, derivation of power to the outlet and, on the other, to the main drive body, it is required that the pulley connected to the motor shaft is arranged as closely as possible to the maximum diameter and that the sun and the differential satellite carrier are interlocked.
The fact that there are no relative speeds between the coupling bodies enables the clutches such as those used in the state of the art to be dispensed with when they are designed to absorb different relative speeds.
In the forward gear, in order to increase the outlet variation range the fact that the differential outlet speed is zero when the motor pulley approximates to the range of minimum diameter is taken advantage of to stop the epicyclical gear satellite carrier with the interlocking mechanism at zero speed of the intermediate shaft, that is, with without friction. In this way a different transmission ratio is applied which enables the motor pulley to be varied in the opposite direction however, continually increasing the speed of the mechanism outlet.
In addition, in order to obtain reverse movement the pulley attached to the motor shaft should be positioned at its maximum diameter with the satellite carrier interlock disconnected and with the sun joined to the satellite carrier.
To summarise, this means of working with continual speed variation is as follows:
Rotation at
the outlet of
the final Diameter of Sun-satellite Satellite
epicyclical the power carrier carrier
gear pulley interlock Interlock
Reverse Maximum Connected Disconnected
Stopped Close to Connected Disconnected
maximum
Forward Reducing Connected Disconnected
Forward rapid Close to Connected Disconnected
and close to minimum
intermediate
range
Intermediate Minimum Disconnected Connected
range (outlet
speed of the
differential
shaft = 0
Increasing Increasing to Disconnected Connected
speed to the the maximum
maximum
DESCRIPTION OF THE DRAWINGS
The present descriptive report is complemented by a set of plans illustrating a preferred embodiment of the invention but which is in no way restrictive.
FIG. 1 shows a diagram of the transmission according to a preferred embodiment of the three interconnected epicyclical gears of the invention.
 PREFERRED EMBODIMENT OF THE INVENTION
The present invention refers to a continually variable transmission, of the type of transmission means using variable speed device and in particular, one of these having a conical surface as well as incorporating epicyclical gears.
In accordance with the preferred embodiment of FIG. 1, an external drive (1) is coupled to the variable speed device (2) and (3) connected to an epicyclical gear (5) partially receiving the power from the motor shaft, by means of a gear pinion (4) and with the tapered pulley (2) connected to the crown wheel (5.1) through transmission means (10) and (11) in this example, of the epicyclic gear (5) while the other pulley (3) is linked to the sun (5.2) and the satellite carrier (5.3) transmits this power to a subsequently arranged epicyclic gear (6) coupled or interlocked (6.5) with the satellite carrier (6.2) of the epicyclic gear (6), in addition the satellite carrier (6.2) is coupled to an interlock (6.3) and its crown wheel (6.4) is connected to the sun (7.1) of the epicyclic gear (7) the satellite carrier of which (7.2) is in turn connected to the outlet shaft (8) of the transmission, thus deriving from this the aforementioned fraction of the entry power to the two pulleys (2) and (3) while the crown wheel (7.3) of this third epicyclical gear (7) is made with the gear pinion (9) of the entry shaft.
In order to reduce the speed of the outlet shaft (8) of the epicyclic gear (7) to zero in any direction it is essential that the pulley (3) connected to the motor shaft is arranged close to the maximum diameter and that the sun (6.1) and the satellite carrier (6.2) of the epicyclic gear (6) are interlocked.
In order to obtain reverse gear, the pulley (3) should be positioned at its maximum diameter, with the interlocking (6.3) of the satellite carrier (6.2) disconnected and connecting the interlock (6.5).
In the forward gear, a progression of pulley (3) diameters is made from the diameter closest to maximum to the diameter closest to minimum and with the interlocking (6.3) of the satellite carrier (6.2) disconnected and connected to the interlock (6.5). In order to increase the outlet variation range, the fact that the satellite carrier (5.3) outlet speed is zero when the pulley (3) approximates to its range of minimum diameter is taken advantage of to stop the epicyclical gear satellite carrier (6.2) with the interlocking mechanism (6.3) at zero speed of the intermediate shaft.
In order to further increase the range of actuation the pulley (3) progression is varied in the inverse direction, that is, from its minimum diameter to its maximum diameter.
The aforementioned mechanical transmission effectively generates a continual reduction, either a continual multiplication or a continual transmission ratio of 1:1.
In applications with low torque requirement and/or reduced variation range, the epicyclical gear (6) may be dispensed with, thus joining the satellite carrier (5.3) of the epicyclical gear (5) with the sun (7.1) of the epicyclical gear (7).
The essential nature of this invention is not altered by any variations in materials, form, size and arrangement of its component elements, described in a non-restrictive manner, with this being sufficient to proceed to its reproduction by an expert.

Claims (8)

1. A continuously variable transmission, comprising:
a continuously variable speed device;
the continuously variable speed device comprising a first epicyclic gear and a variator of a belt type with a first and a second pulley;
the first epicyclic gear is coupled to the first and second pulley and to an intermediate shaft;
the variable speed device is able to reduce the rotation speed of the intermediate shaft to zero from either rotation direction;
the continuously variable transmission further comprising an entry shaft, a reducer and a second epicyclical gear;
the entry shaft is coupled to the first pulley of the belt type variator and to the second epicyclic gear;
the reducer is placed axially between the first and second epicyclic gear and is coupled to the intermediate shaft and the second epicyclic gear;
a final outlet shaft of the continuously variable transmission is coupled to the second epicyclic gear;
the speed of the final outlet shaft may be varied in any rotation direction and to zero by means of a combination of different diameters of the first pulley together with various forms of interlocking of reducer elements generating either a reducer transmission ratio of 1:1 or a different reducer transmission ratio;
wherein:
the first pulley is coupled to a sun of the first epicyclical gear;
the second pulley is coupled to a crown wheel of the first epicyclic gear through transmission means;
the reducer is an epicyclic gear;
the intermediate shaft is coupled to a satellite carrier of the first epicyclic gear and to a sun of the reducer;
a crown wheel of the reducer is coupled to a sun of the second epicyclic gear;
a satellite carrier of the second epicyclic gear is coupled to the final outlet shaft;
the entry shaft having a first and a second gear pinion;
a crown wheel of the second epicyclic gear is coupled to the second gear pinion of the entry shaft;
the first pulley is coupled to the entry shaft by a first gear pinion;
the reducer generating a reducer transmission ratio of 1:1 when the sun and a satellite carrier of the reducer are interlocked or generating a different reducer transmission ratio when the satellite carrier is stopped by an interlocking mechanism.
2. A continuously variable transmission, comprising:
a drive shaft;
a first gear pinion;
a variable speed device comprising a first tapered pulley and a second tapered pulley;
said first gear pinion coupling said drive shaft to said first tapered pulley;
a first epicyclic gear having a first epicyclic gear crown, a first epicyclic gear sun, and a first epicyclic gear satellite;
said first tapered pulley coupled to said first epicyclic gear sun;
said second tapered pulley coupled to said first epicyclic gear crown;
a second epicyclic gear having a second epicyclic gear satellite carrier, a second epicyclic gear satellite first couple or interlock, a second epicyclic gear satellite second interlock, and a second epicyclic gear satellite crown wheel;
said first epicyclic gear satellite coupling said first epicyclic gear sun and said first epicyclic gear crown to said second epicyclic gear satellite first couple or interlock;
second epicyclic gear satellite carrier coupled to said second epicyclic gear satellite second interlock;
a third epicyclic gear having a third epicyclic gear satellite carrier, a third epicyclic gear sun, a third epicyclic gear crown wheel;
said second epicyclic gear satellite crown wheel connected to said third epicyclic gear sun;
a second gear pinion;
said second gear pinion coupling said drive shaft to said third epicyclic gear crown wheel;
an outlet shaft; and
said third epicyclic gear satellite carrier connected to said outlet shaft.
3. The transmission of claim 2 wherein said second epicyclic gear sun and said second epicyclic gear satellite carrier are interlocked using a function of said second epicyclic gear satellite first couple or interlock.
4. The transmission of claim 2 wherein said second epicyclic gear satellite second interlock is disconnected from said second epicyclic gear satellite first couple or interlock.
5. The transmission of claim 2 which excludes a clutch.
6. A method of using a continuously variable transmission, said continuously variable transmission comprising:
a drive shaft;
a first gear pinion;
a variable speed device comprising a first tapered pulley and a second tapered pulley;
said first gear pinion coupling said drive shaft to said first tapered pulley;
a first epicyclic gear having a first epicyclic gear crown, a first epicyclic gear sun, and a first epicyclic gear satellite;
said first tapered pulley coupled to said first epicyclic gear sun;
said second tapered pulley coupled to said first epicyclic gear crown;
a second epicyclic gear having a second epicyclic gear satellite carrier, a second epicyclic gear satellite first couple or interlock, a second epicyclic gear satellite second interlock, and a second epicyclic gear satellite crown wheel;
said first epicyclic gear satellite coupling said first epicyclic gear sun and said first epicyclic gear crown to said second epicyclic gear satellite first couple or interlock;
second epicyclic gear satellite carrier coupled to said second epicyclic gear satellite second interlock;
a third epicyclic gear having a third epicyclic gear satellite carrier, a third epicyclic gear sun, a third epicyclic gear crown wheel;
said second epicyclic gear satellite crown wheel connected to said third epicyclic gear sun;
a second gear pinion;
said second gear pinion coupling said drive shaft to said third epicyclic gear crown wheel;
an outlet shaft; and
said third epicyclic gear satellite carrier connected to said outlet shaft;
said method comprising rotating said outlet shaft.
7. The method of claim 6 further comprising reducing the rotation of said outlet shaft comprising interlocking said second epicyclic gear sun and said second epicyclic gear satellite carrier.
8. The method of claim 6 further comprising reversing direction of rotation of said outlet shaft comprising disconnecting said second epicyclic gear satellite second interlock and said second epicyclic gear satellite first couple or interlock.
US11/916,484 2005-06-06 2005-06-06 Continually variable transmission Expired - Fee Related US8226518B2 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/ES2005/070085 WO2006131574A1 (en) 2005-06-06 2005-06-06 Continually-variable transmission

Publications (2)

Publication Number Publication Date
US20090023532A1 US20090023532A1 (en) 2009-01-22
US8226518B2 true US8226518B2 (en) 2012-07-24

Family

ID=37498148

Family Applications (1)

Application Number Title Priority Date Filing Date
US11/916,484 Expired - Fee Related US8226518B2 (en) 2005-06-06 2005-06-06 Continually variable transmission

Country Status (8)

Country Link
US (1) US8226518B2 (en)
EP (1) EP1898123B1 (en)
AT (1) ATE477435T1 (en)
DE (1) DE602005022947D1 (en)
ES (1) ES2351797T3 (en)
PL (1) PL1898123T3 (en)
PT (1) PT1898123E (en)
WO (1) WO2006131574A1 (en)

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150141193A1 (en) * 2013-11-18 2015-05-21 Powertrack Internacional De Automocion, S.L. Continuous and reversible mechanical gear system with a power branch
WO2015073883A1 (en) * 2013-11-18 2015-05-21 Dana Limited Infinite variable transmission with planetary gear set
US9052000B2 (en) 2012-09-07 2015-06-09 Dana Limited Ball type CVT/IVT including planetary gear sets
US9194472B2 (en) 2013-03-14 2015-11-24 Dana Limited Ball type continuously variable transmission
US9222560B2 (en) * 2014-04-21 2015-12-29 Gm Global Technology Operations, Llc Two mode continuously variable transmission
US9347532B2 (en) 2012-01-19 2016-05-24 Dana Limited Tilting ball variator continuously variable transmission torque vectoring device
US9353842B2 (en) 2012-09-07 2016-05-31 Dana Limited Ball type CVT with powersplit paths
US9404414B2 (en) 2013-02-08 2016-08-02 Dana Limited Internal combustion engine coupled turbocharger with an infinitely variable transmission
US9416858B2 (en) 2012-09-07 2016-08-16 Dana Limited Ball type continuously variable transmission/infinitely variable transmission
US9541179B2 (en) 2012-02-15 2017-01-10 Dana Limited Transmission and driveline having a tilting ball variator continuously variable transmission
US9551404B2 (en) 2013-03-14 2017-01-24 Dana Limited Continuously variable transmission and an infinitely variable transmission variator drive
US9556943B2 (en) 2012-09-07 2017-01-31 Dana Limited IVT based on a ball-type CVP including powersplit paths
US9556941B2 (en) 2012-09-06 2017-01-31 Dana Limited Transmission having a continuously or infinitely variable variator drive
US9599204B2 (en) 2012-09-07 2017-03-21 Dana Limited Ball type CVT with output coupled powerpaths
US9638296B2 (en) 2012-09-07 2017-05-02 Dana Limited Ball type CVT including a direct drive mode
US9777815B2 (en) 2013-06-06 2017-10-03 Dana Limited 3-mode front wheel drive and rear wheel drive continuously variable planetary transmission
US10030594B2 (en) 2015-09-18 2018-07-24 Dana Limited Abuse mode torque limiting control method for a ball-type continuously variable transmission
US10030748B2 (en) 2012-11-17 2018-07-24 Dana Limited Continuously variable transmission
US10088022B2 (en) 2013-11-18 2018-10-02 Dana Limited Torque peak detection and control mechanism for a CVP

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8382631B2 (en) * 2010-07-21 2013-02-26 Ford Global Technologies, Llc Accessory drive and engine restarting system
US8475316B2 (en) * 2010-07-22 2013-07-02 Ford Global Technologies, Llc Accessory drive and engine restarting system
US8282351B2 (en) 2011-11-16 2012-10-09 General Electric Company Split load path gearbox

Citations (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3479908A (en) 1966-04-06 1969-11-25 Deere & Co Combined variable-speed and planetary drive
US3489036A (en) 1967-12-29 1970-01-13 Gen Electric Hydromechanical transmission
GB1515687A (en) 1975-11-15 1978-06-28 Gkn Transmissions Ltd Transmission assemblies
DE3538343A1 (en) * 1984-11-02 1986-05-15 Volkswagen AG, 3180 Wolfsburg Transmission arrangement for vehicles, in particular motor vehicles
US4602525A (en) * 1984-04-27 1986-07-29 Aisin Warner Kabushiki Kaisha Continuously variable speed transmission for a vehicle having a forward-reverse changeover mechanism
US5112283A (en) * 1989-09-04 1992-05-12 Bando Chemical Industries, Ltd. Continuous speed-shifting device
US5183444A (en) * 1991-06-28 1993-02-02 Borg-Warner Automotive Inc. Continuously variable transmission
EP0541771A1 (en) 1991-05-31 1993-05-19 Aragonesa De Equipamientos Para Automoviles, S.A. Adepasa Continuously variable transmission
US5853343A (en) * 1996-09-05 1998-12-29 Ford Global Technologies, Inc. Dual mode continually variable transmission
US5890987A (en) * 1996-02-05 1999-04-06 Van Doorne's Transmissie B.V. Continuously variable transmission
US6106428A (en) * 1998-03-23 2000-08-22 Ford Global Technologies, Inc. Compact dual mode continually variable transmission
US6358178B1 (en) * 2000-07-07 2002-03-19 General Motors Corporation Planetary gearing for a geared neutral traction drive
US6447422B1 (en) * 2001-01-16 2002-09-10 General Motors Corporation Dual mode, geared neutral continuously variable transmission
US6561942B2 (en) * 2001-06-11 2003-05-13 General Motors Corporation Dual mode variable ratio transmission
US6648787B1 (en) 2002-05-23 2003-11-18 General Motors Corporation Traction drive transmission
US20040082421A1 (en) 2002-10-24 2004-04-29 Jurgen Wafzig Split performance power train
US20040166984A1 (en) * 2002-12-05 2004-08-26 Nsk Ltd. Continuously variable transmission apparatus

Patent Citations (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3479908A (en) 1966-04-06 1969-11-25 Deere & Co Combined variable-speed and planetary drive
US3489036A (en) 1967-12-29 1970-01-13 Gen Electric Hydromechanical transmission
GB1515687A (en) 1975-11-15 1978-06-28 Gkn Transmissions Ltd Transmission assemblies
US4602525A (en) * 1984-04-27 1986-07-29 Aisin Warner Kabushiki Kaisha Continuously variable speed transmission for a vehicle having a forward-reverse changeover mechanism
DE3538343A1 (en) * 1984-11-02 1986-05-15 Volkswagen AG, 3180 Wolfsburg Transmission arrangement for vehicles, in particular motor vehicles
US5112283A (en) * 1989-09-04 1992-05-12 Bando Chemical Industries, Ltd. Continuous speed-shifting device
EP0541771A1 (en) 1991-05-31 1993-05-19 Aragonesa De Equipamientos Para Automoviles, S.A. Adepasa Continuously variable transmission
US5183444A (en) * 1991-06-28 1993-02-02 Borg-Warner Automotive Inc. Continuously variable transmission
US5890987A (en) * 1996-02-05 1999-04-06 Van Doorne's Transmissie B.V. Continuously variable transmission
US5853343A (en) * 1996-09-05 1998-12-29 Ford Global Technologies, Inc. Dual mode continually variable transmission
US6106428A (en) * 1998-03-23 2000-08-22 Ford Global Technologies, Inc. Compact dual mode continually variable transmission
US6358178B1 (en) * 2000-07-07 2002-03-19 General Motors Corporation Planetary gearing for a geared neutral traction drive
US6447422B1 (en) * 2001-01-16 2002-09-10 General Motors Corporation Dual mode, geared neutral continuously variable transmission
US6561942B2 (en) * 2001-06-11 2003-05-13 General Motors Corporation Dual mode variable ratio transmission
US6648787B1 (en) 2002-05-23 2003-11-18 General Motors Corporation Traction drive transmission
US20040082421A1 (en) 2002-10-24 2004-04-29 Jurgen Wafzig Split performance power train
US20040166984A1 (en) * 2002-12-05 2004-08-26 Nsk Ltd. Continuously variable transmission apparatus

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
Dec. 14, 2006, ISR of PCT/ES2005/070085.

Cited By (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9347532B2 (en) 2012-01-19 2016-05-24 Dana Limited Tilting ball variator continuously variable transmission torque vectoring device
US9541179B2 (en) 2012-02-15 2017-01-10 Dana Limited Transmission and driveline having a tilting ball variator continuously variable transmission
US9556941B2 (en) 2012-09-06 2017-01-31 Dana Limited Transmission having a continuously or infinitely variable variator drive
US9353842B2 (en) 2012-09-07 2016-05-31 Dana Limited Ball type CVT with powersplit paths
US10006527B2 (en) 2012-09-07 2018-06-26 Dana Limited Ball type continuously variable transmission/infinitely variable transmission
US9599204B2 (en) 2012-09-07 2017-03-21 Dana Limited Ball type CVT with output coupled powerpaths
US9689477B2 (en) 2012-09-07 2017-06-27 Dana Limited Ball type continuously variable transmission/infinitely variable transmission
US9416858B2 (en) 2012-09-07 2016-08-16 Dana Limited Ball type continuously variable transmission/infinitely variable transmission
US9052000B2 (en) 2012-09-07 2015-06-09 Dana Limited Ball type CVT/IVT including planetary gear sets
US9638296B2 (en) 2012-09-07 2017-05-02 Dana Limited Ball type CVT including a direct drive mode
US9556943B2 (en) 2012-09-07 2017-01-31 Dana Limited IVT based on a ball-type CVP including powersplit paths
US10088026B2 (en) 2012-09-07 2018-10-02 Dana Limited Ball type CVT with output coupled powerpaths
US10030748B2 (en) 2012-11-17 2018-07-24 Dana Limited Continuously variable transmission
US9404414B2 (en) 2013-02-08 2016-08-02 Dana Limited Internal combustion engine coupled turbocharger with an infinitely variable transmission
US9644530B2 (en) 2013-02-08 2017-05-09 Dana Limited Internal combustion engine coupled turbocharger with an infinitely variable transmission
US9933054B2 (en) 2013-03-14 2018-04-03 Dana Limited Continuously variable transmission and an infinitely variable transmission variator drive
US9638301B2 (en) 2013-03-14 2017-05-02 Dana Limited Ball type continuously variable transmission
US9689482B2 (en) 2013-03-14 2017-06-27 Dana Limited Ball type continuously variable transmission
US9551404B2 (en) 2013-03-14 2017-01-24 Dana Limited Continuously variable transmission and an infinitely variable transmission variator drive
US9194472B2 (en) 2013-03-14 2015-11-24 Dana Limited Ball type continuously variable transmission
US9777815B2 (en) 2013-06-06 2017-10-03 Dana Limited 3-mode front wheel drive and rear wheel drive continuously variable planetary transmission
US20150141193A1 (en) * 2013-11-18 2015-05-21 Powertrack Internacional De Automocion, S.L. Continuous and reversible mechanical gear system with a power branch
US10001200B2 (en) * 2013-11-18 2018-06-19 Powertrack Internacional De Automocion, S.L. Continuous and reversible mechanical gear system with a power branch
US10030751B2 (en) 2013-11-18 2018-07-24 Dana Limited Infinite variable transmission with planetary gear set
US10088022B2 (en) 2013-11-18 2018-10-02 Dana Limited Torque peak detection and control mechanism for a CVP
WO2015073883A1 (en) * 2013-11-18 2015-05-21 Dana Limited Infinite variable transmission with planetary gear set
US9222560B2 (en) * 2014-04-21 2015-12-29 Gm Global Technology Operations, Llc Two mode continuously variable transmission
US10030594B2 (en) 2015-09-18 2018-07-24 Dana Limited Abuse mode torque limiting control method for a ball-type continuously variable transmission

Also Published As

Publication number Publication date
ATE477435T1 (en) 2010-08-15
ES2351797T3 (en) 2011-02-10
EP1898123A1 (en) 2008-03-12
EP1898123B1 (en) 2010-08-11
PL1898123T3 (en) 2011-10-31
WO2006131574A1 (en) 2006-12-14
PT1898123E (en) 2010-11-18
DE602005022947D1 (en) 2010-09-23
US20090023532A1 (en) 2009-01-22

Similar Documents

Publication Publication Date Title
US8226518B2 (en) Continually variable transmission
US6761658B1 (en) Four mode hydro-mechanical transmission
RU2487284C2 (en) Infinitely variable transmission
CA2344870C (en) Hydro-mechanical transmission
US6905434B2 (en) Speed change mechanism of automatic transmission
US20050176547A1 (en) Continuously variable transmission system
CN103557289A (en) Toroidal traction drive transmission
US4258585A (en) Four-range hydromechanical transmission with hydrostatic steering module
US20080146399A1 (en) Continuously Variable Ratio Transmission
US11815169B2 (en) Transmission, drive train and vehicle having a transmission
CN106337920A (en) Dual clutch continuously variable transmission
US5471892A (en) Multi-speed parallel axis three countershafts and an output shaft power transmission
DE04764114T1 (en) HYDROMECHANICAL GEARBOX FOR AGRICULTURAL TRACTORS
JPS6250695B2 (en)
US5888161A (en) All wheel drive continuously variable transmission having dual mode operation
JPH04501163A (en) Continuously variable transmission
US4673377A (en) Belt-pulley type steplessly variable transmission having a reverse drive gear mechanism
KR101326368B1 (en) Transmission of vehicle
EP0157050A1 (en) Multi-pass continuously variable transmission
EP1633996B1 (en) Additive gearshift with differential gears
US10234005B2 (en) Device for continuously variable transmission
JP6123733B2 (en) Vehicle transmission
JPS5934058A (en) Power transmission device
RU2137619C1 (en) Vehicle hydromechanical gearbox
JPH02240444A (en) Transmission for vehicle

Legal Events

Date Code Title Description
AS Assignment

Owner name: POWER GEAR S.L., SPAIN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:GIMENO, JAVIER PARRAGA;REEL/FRAME:020232/0546

Effective date: 20071130

AS Assignment

Owner name: POWERTRACK INTERNATIONAL DE AUTOMOCION S.L., SPAIN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:POWER GEAR S.L.;REEL/FRAME:027123/0434

Effective date: 20101001

FEPP Fee payment procedure

Free format text: PAYOR NUMBER ASSIGNED (ORIGINAL EVENT CODE: ASPN); ENTITY STATUS OF PATENT OWNER: SMALL ENTITY

FEPP Fee payment procedure

Free format text: PAYER NUMBER DE-ASSIGNED (ORIGINAL EVENT CODE: RMPN); ENTITY STATUS OF PATENT OWNER: SMALL ENTITY

Free format text: PAYOR NUMBER ASSIGNED (ORIGINAL EVENT CODE: ASPN); ENTITY STATUS OF PATENT OWNER: SMALL ENTITY

STCF Information on status: patent grant

Free format text: PATENTED CASE

CC Certificate of correction
FPAY Fee payment

Year of fee payment: 4

FEPP Fee payment procedure

Free format text: MAINTENANCE FEE REMINDER MAILED (ORIGINAL EVENT CODE: REM.); ENTITY STATUS OF PATENT OWNER: SMALL ENTITY

LAPS Lapse for failure to pay maintenance fees

Free format text: PATENT EXPIRED FOR FAILURE TO PAY MAINTENANCE FEES (ORIGINAL EVENT CODE: EXP.); ENTITY STATUS OF PATENT OWNER: SMALL ENTITY

STCH Information on status: patent discontinuation

Free format text: PATENT EXPIRED DUE TO NONPAYMENT OF MAINTENANCE FEES UNDER 37 CFR 1.362